EP4081414B1 - Appareil de commande - Google Patents

Appareil de commande Download PDF

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Publication number
EP4081414B1
EP4081414B1 EP21707964.9A EP21707964A EP4081414B1 EP 4081414 B1 EP4081414 B1 EP 4081414B1 EP 21707964 A EP21707964 A EP 21707964A EP 4081414 B1 EP4081414 B1 EP 4081414B1
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EP
European Patent Office
Prior art keywords
valve
valve piston
suspension
piston
control device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21707964.9A
Other languages
German (de)
English (en)
Other versions
EP4081414A1 (fr
EP4081414B8 (fr
EP4081414C0 (fr
Inventor
Heinz-Peter Huth
Johannes MERSCHER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydac Mobilhydraulik GmbH
Original Assignee
Hydac Mobilhydraulik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Publication of EP4081414A1 publication Critical patent/EP4081414A1/fr
Publication of EP4081414B1 publication Critical patent/EP4081414B1/fr
Publication of EP4081414C0 publication Critical patent/EP4081414C0/fr
Application granted granted Critical
Publication of EP4081414B8 publication Critical patent/EP4081414B8/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
    • B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
    • B60G17/056—Regulating distributors or valves for hydropneumatic systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G11/00—Resilient suspensions characterised by arrangement, location or kind of springs
    • B60G11/26—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs
    • B60G11/265—Resilient suspensions characterised by arrangement, location or kind of springs having fluid springs only, e.g. hydropneumatic springs hydraulic springs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/06—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid
    • B60G21/067—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid between wheels on different axles on the same side of the vehicle, i.e. the left or the right side
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
    • B60G21/06—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid
    • B60G21/073—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid between wheels on the same axle but on different sides of the vehicle, i.e. the left and right wheel suspensions being interconnected
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
    • B60G21/10—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces not permanently interconnected, e.g. operative only on acceleration, only on deceleration or only at off-straight position of steering
    • B60G21/106—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces not permanently interconnected, e.g. operative only on acceleration, only on deceleration or only at off-straight position of steering transversally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/10—Type of spring
    • B60G2202/15—Fluid spring
    • B60G2202/154—Fluid spring with an accumulator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/40—Auxiliary suspension parts; Adjustment of suspensions
    • B60G2204/46—Means for locking the suspension
    • B60G2204/4605—Means for locking the suspension hydraulically, e.g. interrupting communication between the chambers of a hydraulic cylinder
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/80—Interactive suspensions; arrangement affecting more than one suspension unit
    • B60G2204/82—Interactive suspensions; arrangement affecting more than one suspension unit left and right unit on same axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
    • B60G2204/80—Interactive suspensions; arrangement affecting more than one suspension unit
    • B60G2204/83—Type of interconnection
    • B60G2204/8304—Type of interconnection using a fluid
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2400/00—Indexing codes relating to detected, measured or calculated conditions or factors
    • B60G2400/50—Pressure
    • B60G2400/51—Pressure in suspension unit

Definitions

  • the invention relates to a control device for a pendulum axle suspension, in particular a front axle suspension, with the features of claim 1.
  • the known axle suspension is not designed to swing, so that no roll stabilization is provided for such swinging movements.
  • front axle suspensions based on independent wheel suspension have been implemented, which enable swinging operation of the front axle and thus also provide roll stabilization as well as locking and releasing the axle suspension;
  • the known solutions alone require a large number of individual valves that have to interact with one another, which impairs functional reliability.
  • the implementation of the known solutions is complex and therefore costly.
  • a valve device consisting of at least one valve piston arranged in a valve housing so as to be longitudinally displaceable along a travel axis by means of an electric motor, which at least partially connects or separates fluid connection points arranged in the valve housing, such as a pressure supply connection and two utility connections for a hydraulic consumer, so that the valve piston within the valve housing can be controlled in a positionally precise manner for sensible operation via a conventional electric motor with appropriate control by means of an assignable computer unit.
  • the US 2001/0024021 A1 describes a control device for a pendulum axle suspension, in particular a front axle suspension, the control device consisting of at least one hydraulic accumulator device, a suspension device and a valve to which the two devices are connected via fluid connection points, wherein the valve controls the fluid connection points in such a way that the axle oscillation occurs in at least one functional position of the valve piston when the suspension is locked and the suspension occurs in at least one further second functional position of the valve piston when the axle oscillation is locked.
  • the invention is based on the object of further improving the known control device in such a way that a pendulum-type axle suspension, in particular a front axle suspension, is obtained in a cost-effective manner with few components, which is also functionally reliable in use.
  • the valve is designed as a proportional valve, that a valve piston is guided longitudinally in a valve housing of the proportional valve and can be actuated by an electric motor, and that in a further third functional position of the valve piston, the axle oscillation and pressure equalization between the hydraulic accumulator device and the suspension device take place.
  • valve piston is guided longitudinally in a valve housing of the pilot valve and can be actuated by an electric motor and controls the fluid connection points in such a way that in at least one functional position of the valve piston when the suspension is locked, the axle oscillation occurs and in at least one further second functional position of the valve piston when the axle oscillation is locked, all the adjustment processes required for the oscillation and springing of the axle suspension, including locking of the same, can in principle be carried out with just one single proportional valve controlled by the electric motor. This has no equivalent in the state of the art.
  • the proportional transition from the first functional position of the valve piston, in which the axle swings when the suspension is locked, to the second functional position, in which the suspension is locked when the axle swings, achieves pressure equalization between the hydraulic accumulator device and the suspension device.
  • the first functional position of the valve piston can be designed to be "slide-tight" for the purpose of pressure equalization, without the need for devices to reduce the flow cross-section, such as nozzles, in a bypass.
  • the proportionality of the valve enables variable damping of the suspension to be achieved.
  • the transitions between the individual functional positions are designed to be "harmonious", so that undesirable, jerky movements of the associated working machine are avoided.
  • the hydraulic accumulator device is formed from two, preferably identically designed, hydraulic accumulators, each of which is connected with its liquid side to a fluid connection point in the valve housing, and that the valve piston controls the respective fluid-carrying connection to two further fluid connection points in the valve housing, to each of which a suspension cylinder of the suspension device is connected, preferably with its piston side.
  • valve housing has two additional fluid connection points that can be controlled by the valve piston and locked in at least one of the functional positions, one of which is connected to the piston side of one suspension cylinder and the other to the piston side of the other suspension cylinder.
  • the proportional valve is designed with multiple connection technology, making it particularly suitable for large volume flows.
  • the electric motor acts on a pinion drive of the valve piston via a gear arranged in a gear chamber, which is penetrated by a longitudinal channel and creates a pressure equalization between the gear chamber and a tank or return connection in the valve housing.
  • the pressure equalization allows the valve piston to be brought into its functional positions in a pressure-balanced manner, and can be moved by means of the electric motor via the pinion drive with a particularly high resolution in relation to the fluid connection points.
  • the electric motor can be controlled by a computer unit that receives at least sensor information from at least two pressure sensors, each of which is connected to a fluid-carrying connection between the valve piston and the respective suspension cylinder and/or the valve piston and the respective hydraulic accumulator.
  • the cylinder pressure in this suspension cylinder can be detected by means of a respective pressure sensor connected to the fluid connection between the valve piston and the respective suspension cylinder, whereby the axle load can be determined indirectly.
  • the differential pressure in the locked state of the suspension can be determined for the purpose of checking or monitoring pressure equalization.
  • the respective sensor can be part of the respective hydraulic accumulator or the respective suspension cylinder, in particular can be arranged in it.
  • the electric motor moves the valve piston in two directions arranged in opposite directions in the valve housing. This enables a compact valve construction.
  • control device Due to the fact that the electric motor with its gear housing is preferably accommodated in a drive housing and is arranged on one end face of the valve housing free of fluid connection points, the control device is designed to be particularly space-saving and can be connected in a side-by-side arrangement with other control devices to form control blocks.
  • a control unit in the form of integrated electronics can be provided on the valve, which is connected to a CAN bus and controls the electric motor.
  • integrated electronics free up two power outputs on the controller and reduce the assembly and wiring effort.
  • the power consumption for a movement of the valve piston is low.
  • the design of the valve piston actuating device makes it possible for the valve piston to remain in its current functional position, for example when the actuating device is de-energized, until it is moved to a different position using the electric motor, which proves to be advantageous in terms of energy and which also improves the safety of the actuating device.
  • Fig. 1 and 3 relate to a first embodiment of a control device according to the invention for a pendulum axle suspension in the form of a front axle suspension.
  • the control device has a hydraulic accumulator device 10, a suspension device 12 and a proportional valve 14.
  • the hydraulic accumulator device 10 and the suspension device 12 are connected to fluid connection points 16, 18, 20, 22 of the proportional valve 14.
  • the proportional valve 14 has a valve housing 24 in which a valve piston 26 is guided so as to be longitudinally movable.
  • the valve piston 26 can be actuated by an electric motor 28 and controls the fluid connection points 16, 18, 20, 22 such that in a first functional position of the valve piston 26, when the suspension is locked, the axle oscillation is activated and in a second functional position of the valve piston 26, when the axle oscillation is locked, the suspension is activated.
  • valve piston 26 controls the fluid connection points 16, 18, 20, 22 in such a way that in a third functional position of the valve piston 26 the axle oscillation is activated and pressure equalization takes place between the hydraulic accumulator device 10 and the suspension device 12.
  • a fourth functional position of the valve piston 26 is provided in which both the axle oscillation and the suspension are activated.
  • the valve piston 26 has a fifth functional position in which proportional damping for the suspension device 12 takes place when the axle oscillation is blocked.
  • the valve housing 24 has a main housing part 30, through which a passage 32 extends, in which the valve piston 26 is guided so as to be longitudinally displaceable along its longitudinal axis 34.
  • the passage 32 of the main housing part 30 is widened in the direction away from the valve piston 26, forming a step 38 and a conical extension 40 following the step 38 in the inner diameter 42.
  • the conical extension 40 is in the middle region of the passage extension 44 between the step 38 and the one end 46 of the passage 32 of the main housing part 30.
  • the valve piston 26 is spaced from the main housing part 30.
  • An insert part 48 is introduced into the passage extension 44 as part of the valve housing 24.
  • the insert part 48 has an extension of its outer diameter in the direction away from the valve piston 26 corresponding to the conical inner circumferential extension 40 of the passage 32 of the main housing part 30 and an end-side, annular projection 52 which extends completely in the radial direction from the end 60 of the insert part 48 facing away from the valve piston 26.
  • the outer diameter 53 of the annular projection 52 of the insert part 48 is larger than the largest inner diameter 42 of the passage 32 of the main housing part 30.
  • the insert part 48 In a state in which the insert part 48 is fixed in the main housing part 30 via a threaded section 54, the insert part 48 is in contact with an outer wall 56 of the main housing part 30 with its annular projection 52 and with its front end 58 facing the valve piston 26 in contact with the step 38 of the passage 32 of the main housing part 30.
  • the threaded section 54 between the insert part 48 and the main housing part 30 is provided, viewed in the axial direction, between the conical passage extension 40 and the end 60 of the passage 32 of the main housing part 30 facing away from the valve piston 26.
  • An annular groove 62 is formed in the outer circumference 61 of the insert part 48 between its end 58 facing the valve piston 26 and its central region, in which a sealing ring 64 is provided which is in sealing contact with the main housing part 30.
  • the insert part 48 has a tank or return connection T on its side 65 facing away from the valve piston 26, from which a central fluid channel 68 extends in the axial direction towards the valve piston 26 through the insert part 48.
  • a central fluid channel 68 extends in the axial direction towards the valve piston 26 through the insert part 48.
  • the inner diameter 73 of the insert part 48 is Accommodating a further sealing ring 72.
  • the stepped inner diameter expansion of the fluid channel 68 is followed in the direction of the end projection 52 of the insert part 48 by a first annular inner diameter reduction 74 of the insert part 48 for guiding the valve piston 26 with an inner diameter that is slightly larger than the outer diameter 76 of the valve piston 26.
  • a second annular inner diameter reduction 80 of the insert part 48 is provided as an end stop for the valve piston 26, which has a smaller inner diameter than the outer diameter 76 of the valve piston 26.
  • the valve piston 26 has a first 82, a second 84 and a third 86 annular recess spaced apart from one another in the axial direction, as seen from its end 87 facing the insert part 48 in the direction of its end 89 facing away from the insert part 48.
  • each recess 82, 84, 86 is trough-shaped or U-shaped.
  • each recess 82, 84, 86 of the valve piston 26, viewed in longitudinal section has a base side 88, from the ends of which extend an inclined side wall part 90 extending outwards in the axial direction and simultaneously in the radial direction, as well as an adjoining radial side wall part 92 extending only in the radial direction.
  • a first 16 and a fourth 22 fluid connection point for the hydraulic accumulator device 10 and a second 18 and a third 20 fluid connection point is provided for the suspension device 12.
  • the fluid connection points 16, 22 for the hydraulic accumulator device 10 and the fluid connection points 18, 20 for the suspension device 12 are connected by a Fig. 3 shown cutting plane, in which the longitudinal axis 34 of the valve piston 26 lies, wherein the fluid connection points 16, 22 for the hydraulic accumulator device 10 are arranged on one side of the longitudinal axis 34 and the fluid connection points 18, 20 for the suspension device 12 are arranged on the other side of the longitudinal axis 34.
  • the hydraulic accumulator device 10 has two hydraulic accumulators 98, 100 which are designed identically.
  • One hydraulic accumulator 98 is connected with its liquid side to the first fluid connection point 16 via a first fluid line 102 and the other hydraulic accumulator 100 is connected with its liquid side to the fourth fluid connection point 22 via a fourth fluid line 104.
  • An orifice plate 106 is provided in each of the first 102 and the fourth 104 fluid lines.
  • the suspension device 12 has two suspension cylinders 108, 110.
  • One suspension cylinder 108 is connected with its piston side via a second fluid line 109 to the second fluid connection point 18 and the other suspension cylinder 110 is connected with its piston side via a third fluid line 111 to the third fluid connection point 20.
  • One suspension cylinder 108 serves to provide suspension for one wheel of the front axle and the other suspension cylinder 110 serves to provide suspension for the other wheel of the front axle.
  • a fluid channel 112 extends through the valve housing 24 to the valve piston 26 and opens into a first 114, second 116, third 118 and fourth 120 control chamber in the valve housing 24, viewed from the end 56 of the valve housing 24 with the insert part 48 in the direction of its the end 123 facing away from the insert part 48.
  • the first fluid connection point 16 is fluidically connected to the first control chamber 114, the second fluid connection point 18 to the second control chamber 116, the third fluid connection point 20 to the third control chamber 118 and the fourth fluid connection point 22 to the fourth control chamber 120.
  • Each control chamber 114, 116, 118, 120 is arranged as part of the passage 32 through the valve housing 24 coaxially to the longitudinal axis 34 of the valve piston 26 and has an inner diameter that is larger than the inner diameter 42 of guide parts 124, 126, 128 of the passage 32 for guiding the valve piston 26, which are provided in particular between two adjacent control chambers 114, 116, 118, 120.
  • the valve piston 26 extends through each of the control chambers 114, 116, 118, 120.
  • a drive housing 132 is connected to the valve housing 24 on the side 123 facing away from the insert part 48 and free of fluid connections, in which the electric motor 28 is arranged such that a fictitious extension of its drive axis intersects the longitudinal axis 34 of the valve piston 26 perpendicularly.
  • a gear chamber 134 is provided in the drive housing 132, in which a drive pinion 136 that can be driven by the electric motor 28 meshes with a rack 138 of the valve piston 26.
  • the rack 138 is attached to the end region 146 of the valve piston 26 facing away from the insert part 48 and extends away from it in the axial direction into the gear chamber 134.
  • the drive pinion 136 and the rack 138 together form a pinion drive.
  • the drive shaft of the electric motor 28 is operatively connected to the drive pinion 136 via a planetary gear, which is provided in a gear housing in the drive housing 130, which is arranged between the electric motor 28 and the drive pinion 136 and is not shown in the figures.
  • planetary gears are known from the prior art. In this regard, reference is made to the DE 10 2015 015 685 A1 referred to.
  • valve piston 26 By means of the electric motor 28, the valve piston 26 can be moved in two opposite directions in the valve housing 24.
  • the inner diameter 42 of the passage 32 is expanded to form an annular groove 142 in which a further sealing ring 144 is provided.
  • the valve piston 26 is reduced in the direction of the drive housing 132 to form a conical diameter reduction 148 in the outer diameter 76.
  • An extension 150 is formed on the end 89 of the valve piston 26 facing the drive housing 132, which has a further passage 152 extending perpendicular to the longitudinal axis 34 of the valve piston 26.
  • the further passage 152 serves to engage an actuating part of an emergency actuating device not shown in the figures.
  • Emergency actuating devices of this type are known from the prior art. In this regard, reference is made to the DE 10 2015 015 685 A1 referred to.
  • a central longitudinal channel 154 extends through the valve piston 26 from its end 87 facing the insert part 48 in the direction of the drive housing 132, which channel merges into a transverse channel 156 in the end region 146 of the valve piston 26 facing the drive housing 132 and has a reduced outer diameter 76, the two ends of which open out of the valve piston 26 into the gear chamber 134 in this region 146.
  • the gear chamber 134 is connected to the tank or return connection T in a fluid-conducting manner via the relevant channel guide 154, 156 in the valve piston 26 and via the fluid channel 68 in the insert part 48 in order to establish pressure equalization.
  • a pressure sensor (not shown in the figures) is connected to the fluid-carrying connections 112, 109, 111 between the valve piston 26 and the respective suspension cylinder 108, 110.
  • the sensor information recorded by the pressure sensors is fed to a computing unit (not shown in the figures), which is provided in the form of integrated electronics in the drive housing 132 and by means of which the electric motor 28 can be controlled.
  • the drive housing 132 has a plug part 158.
  • the guide part 124 is arranged between the first 114 and the second 116 control chamber in the area of the base side 88 of the first recess 82, the guide part 126 is arranged between the second 116 and the third 118 control chamber in the area of the base side 88 of the second recess 84, and the guide part 128 is arranged between the third 118 and the fourth 120 control chamber in the area of the base side 88 of the third recess 86, as seen in the axial direction.
  • the valve piston 26 In the first functional position 1 of the proportional valve 14, the valve piston 26 is moved to its one end position in the direction of the insert part 48, in which it is in contact with the second annular inner diameter reduction 80 of the insert part 48.
  • the guide part 124 of the passage 32 between the first 114 and the second 116 control chamber is in guiding contact with the full outer diameter 76 of the valve piston 26 between its first 82 and second 84 recess.
  • the guide part 128 between the third 118 and the fourth 120 control chamber is in guiding contact with the full outer diameter 76 of the valve piston 26 at its end region 146 facing the drive housing 132.
  • the respective fluid-carrying connection between the hydraulic accumulator device 10 and the suspension device 12 as well as between the hydraulic accumulators 98, 100 is blocked, whereby the suspension is blocked.
  • the second recess 84 of the valve piston 26, viewed in the axial direction, is arranged with its base side 88 in the area of the guide part 126 between the second 116 and the third 118 control chamber, so that a fluid-carrying connection between the two suspension cylinders 108, 110 of the suspension device 12 is established without any constriction in the flow cross-section. Axle oscillation is thus possible when the suspension is blocked.
  • valve piston 26 viewed in the axial direction, is arranged with its full diameter 76 between the first 82 and the second 84 recess slightly offset in the direction of the drive housing 132 relative to the guide part 124 between the first 114 and the second 116 control chamber, so that this guide part 124 is located in the region of the inclined side wall 90 of the first recess 82.
  • This guide part 124 thus forms an orifice with the adjacent second control edge 96 of the first recess 82, which narrows the flow cross-section to and from the one hydraulic accumulator 98.
  • the full diameter 76 of the valve piston 26 is arranged in the axial direction at the end region 146 of the valve piston 26 facing the drive housing 132, slightly offset in the direction of the drive housing 132 from the guide part 128 between the third 118 and the fourth 120 control chamber, which is located in the region of the inclined side wall 90 of the third recess 86.
  • This guide part 128 forms a further aperture with the adjacent second control edge 96 of the third recess 86, which narrows the flow cross-section to and from the other hydraulic accumulator 100. This enables pressure equalization between the hydraulic accumulator device 10 and the suspension device 12.
  • the guide part 126 is arranged between the second 116 and the third 118 control chamber in the area of the base side 88 of the second recess 84, viewed in the axial direction. This creates a fluid-carrying connection from and to each suspension cylinder 108, 110 without any constriction in the flow cross-section, so that the axle oscillation and pressure equalization between the hydraulic accumulator device 10 and the suspension device 12 is possible.
  • the guide part 124 is arranged between the first 114 and the second 116 control chamber in the region of the base side 88 of the first recess 82, the guide part 126 between the second 116 and the third 118 control chamber in leading contact with the full diameter 76 of the valve piston 26 between the first 82 and the second 84 recess and the guide part 128 between the third 118 and the fourth 120 control chamber in the region of the base side 88 of the third recess 86.
  • valve piston 26 viewed in the axial direction, is arranged with its full diameter 76 at its end region facing the insert part 48, slightly offset in the direction of the insert part 48 relative to the guide part 124 between the first 114 and the second 116 control chamber, so that this guide part 124 is located in the region of the inclined side wall 90 of the first recess 82.
  • This guide part thus forms 126 with the adjacent first control edge 94 of the first recess 82 forms an orifice which narrows the flow cross-section to and from the one hydraulic accumulator 98 which is fluidically connected to the one suspension cylinder 108 via the orifice.
  • the full diameter 76 of the valve piston 26 between the second 84 and the third recess 86 is arranged slightly offset in the direction of the insert part 48 to the guide part 128 between the third 118 and the fourth 120 control chamber, which is located in the region of the inclined side wall 90 of the third recess 86.
  • this guide part 128 forms a further orifice with the adjacent first control edge 94 of the third recess 86 which narrows the flow cross-section to and from the other hydraulic accumulator 100 which is fluidically connected to the other suspension cylinder 110 via the further orifice.
  • the orifice and the further orifice have a damping effect in the respective fluid connection.
  • the guide part 126 between the second 116 and the third 118 control chambers is in guiding contact with the full outer diameter 76 of the valve piston 26 between the first 82 and the second recess 84.
  • the fluid-carrying connection between the one hydraulic accumulator 98 and the one suspension cylinder 108 is separated from the further fluid-carrying connection between the other hydraulic accumulator 100 and the other suspension cylinder 110. This enables proportional damping of the suspension when the axle oscillation is blocked.
  • An adjustable stop device for the valve piston 26, which is not shown in the figures, can be provided in the drive housing 132 and limits the maximum stroke of the valve piston 26.
  • control grooves can be introduced into the outer circumference of the valve piston in its areas with the full outer diameter 76, which extend away from its respective recess 82, 84, 86 in the axial direction, in particular tapering in a wedge shape.
  • Stop device and such control grooves are known from the state of the art. In this regard, reference is made to the DE 10 2017 004 531 A1 referred to.
  • Fig. 2 shows a second embodiment of the control device according to the invention, which differs from the first embodiment shown in Fig. 1 and 3 shown, only differs as follows:
  • the valve housing 24 has two additional fluid connection points 174, 178 that can be controlled by means of the valve piston 26.
  • the piston side of one suspension cylinder 108 is connected to one additional fluid connection point 174 via a fifth fluid line 176
  • the piston side of the other suspension cylinder 110 is connected to the other additional fluid connection point 178 via a sixth fluid line 180.
  • the valve piston 26 In its first, second and third functional positions, the valve piston 26 connects the two additional fluid connection points 174, 178 to one another, whereas in its fourth and fifth functional positions, the valve piston 26 separates the two additional fluid connection points 174, 178 from one another.
  • the fluid-carrying connection or separation between the additional fluid connection points 174, 178 of the second embodiment, which is produced by means of the valve piston 26, replaces the fluid-carrying connection between the one hydraulic accumulator 98 and the other hydraulic accumulator 100 or the one suspension cylinder 108 and the other suspension cylinder 110 of the first embodiment.
  • the functional positions of the second embodiment correspond to those of the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Vehicle Body Suspensions (AREA)

Claims (10)

  1. Installation de commande d'une suspension d'essieu réalisée de manière oscillante, en particulier d'une suspension d'essieu avant, l'installation de commande consistant en au moins un dispositif (10) d'accumulateur hydraulique, un dispositif (12) de suspension et une soupape (14) proportionnelle, qui a un piston (26) de soupape et à laquelle les deux dispositifs (10, 12) sont raccordés par des points (16, 18, 20, 22) de raccordement de fluide, dans laquelle le piston (26) de la soupape est, avec possibilité d'être actionné par un moteur (28) électrique, guidé avec possibilité de se déplacer longitudinalement dans un corps (24) de la soupape (14) proportionnelle et commande les points (16, 18, 20, 22) de raccordement de fluide, de manière à ce que, dans au moins une position (1) de fonctionnement du piston (26) de la soupape alors que la suspension est bloquée, ait lieu l'oscillation de l'essieu et, dans au moins une autre deuxième position (2) de fonctionnement du piston (26) de la soupape alors que l'oscillation de l'essieu est bloquée, ait lieu la suspension et, dans une autre troisième position (3) de fonctionnement du piston (26) de la soupape, ait lieu l'oscillation de l'essieu et une compensation de la pression entre le dispositif (10) accumulateur hydraulique et le dispositif (12) de suspension.
  2. Installation de commande suivant la revendication 1, caractérisée en ce que, dans une autre quatrième position (4) de fonctionnement du piston (26) de la soupape, ont lieu à la fois l'oscillation de l'essieu et la suspension.
  3. Installation de commande suivant la revendication 1 ou 2, caractérisée en ce que, dans une position (5) de fonctionnement supplémentaire optionnelle, un amortissement proportionnel du dispositif (12) de suspension a lieu alors que l'oscillation de l'essieu est bloquée.
  4. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que le dispositif (10) accumulateur hydraulique est formé de deux accumulateurs (98, 100) hydrauliques, de préférence de même constitution, qui, par leur côté liquide, sont raccordés à respectivement un point (16, 22) de raccordement de fluide dans le corps (24) de la soupape, et en ce que le piston (26) de la soupape commande la communication fluidique respective vers deux autres points (18, 20) de raccordement de fluide dans le corps (24) de la soupape, où respectivement un vérin (108, 110) de suspension du dispositif (12) de suspension est raccordé, de préférence par son côté piston.
  5. Installation de commande suivant la revendication 4, caractérisée en ce que le corps (24) de la soupape a deux points (174, 178) de raccordement de fluide supplémentaires pouvant être commandés au moyen du piston (26) de la soupape et pouvant être barrés dans au moins l'une des positions de fonctionnement, dont l'un est raccordé au côté piston du un vérin (108) de la suspension et dont l'autre est raccordé au côté piston de l'autre vérin (110) de la suspension.
  6. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que le moteur (28) électrique attaque, par un engrenage disposé dans un espace (134) d'engrenage, un pignon (136, 138) du piston (26) de la soupape qui, traversé par un conduit (154) longitudinal, ménage une compensation de la pression entre l'espace (134) d'engrenage et un raccord (T) de réservoir ou de retour du corps (24) de la soupape.
  7. Installation de commande suivant l'une des revendications 4 à 5, caractérisée en ce que le moteur (28) électrique peut être commandé par une unité informatique, qui reçoit au moins des informations de capteur d'au moins deux capteurs de pression, qui sont montés respectivement en communication fluidique entre le piston (26) de la soupape et le vérin (108, 110) respectif de la suspension et/ou entre le piston (26) de la soupape et l'accumulateur (98, 100) hydraulique respectif.
  8. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que le moteur (28) électrique déplace le piston (26) de la soupape dans le corps (24) de la soupape dans deux sens de déplacement contraires l'un à l'autre.
  9. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que le moteur (28) électrique est, en étant reçu par sa carcasse d'engrenage dans une carcasse (132) d'entraînement, monté sur un côté (123) frontal du corps (24) de la soupape en étant dégagé de points de raccordement de fluide.
  10. Installation de commande suivant l'une des revendications précédentes, caractérisée en ce que le piston (26) de la soupape reste dans sa position (1 à 5) de fonctionnement en cours jusqu'à ce qu'il soit mis en une autre position au moyen du moteur (28) électrique.
EP21707964.9A 2020-03-13 2021-02-23 Appareil de commande Active EP4081414B8 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020001713.4A DE102020001713A1 (de) 2020-03-13 2020-03-13 Ansteuervorrichtung
PCT/EP2021/054449 WO2021180463A1 (fr) 2020-03-13 2021-02-23 Appareil de commande

Publications (4)

Publication Number Publication Date
EP4081414A1 EP4081414A1 (fr) 2022-11-02
EP4081414B1 true EP4081414B1 (fr) 2024-10-16
EP4081414C0 EP4081414C0 (fr) 2024-10-16
EP4081414B8 EP4081414B8 (fr) 2024-12-18

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EP21707964.9A Active EP4081414B8 (fr) 2020-03-13 2021-02-23 Appareil de commande

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Country Link
US (1) US11801725B2 (fr)
EP (1) EP4081414B8 (fr)
DE (1) DE102020001713A1 (fr)
WO (1) WO2021180463A1 (fr)

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DE102024000760A1 (de) * 2024-03-07 2025-09-11 Hydac Mobilhydraulik Gmbh Ventil nebst Federungsvorrichtung
DE102024000759A1 (de) * 2024-03-07 2025-09-11 Hydac Mobilhydraulik Gmbh Ventil

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Also Published As

Publication number Publication date
WO2021180463A1 (fr) 2021-09-16
US20230089947A1 (en) 2023-03-23
EP4081414A1 (fr) 2022-11-02
US11801725B2 (en) 2023-10-31
EP4081414B8 (fr) 2024-12-18
DE102020001713A1 (de) 2021-09-16
EP4081414C0 (fr) 2024-10-16

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